CA2660494A1 - Multi-stage compressor - Google Patents
Multi-stage compressor Download PDFInfo
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- CA2660494A1 CA2660494A1 CA002660494A CA2660494A CA2660494A1 CA 2660494 A1 CA2660494 A1 CA 2660494A1 CA 002660494 A CA002660494 A CA 002660494A CA 2660494 A CA2660494 A CA 2660494A CA 2660494 A1 CA2660494 A1 CA 2660494A1
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- Prior art keywords
- compressor
- stage
- pressure region
- reciprocating piston
- engine
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- 239000007789 gas Substances 0.000 claims abstract description 15
- 238000001816 cooling Methods 0.000 claims description 5
- 241001052209 Cylinder Species 0.000 claims description 3
- 238000001035 drying Methods 0.000 claims description 2
- 238000010276 construction Methods 0.000 description 12
- 230000006835 compression Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 11
- 230000009286 beneficial effect Effects 0.000 description 6
- 230000010355 oscillation Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000009183 running Effects 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000006386 neutralization reaction Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/005—Multi-stage pumps with two cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/02—Multi-stage pumps of stepped piston type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/16—Filtration; Moisture separation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A multi-stage compressor (1) for compressing gases with a low-pressure region (2) and a high-pressure region (5), wherein at least one rotary compressor (3) is provided in the low-pressure region (2), and at least one reciprocating piston compressor (6) with two cylinders (7) is provided in the high-pressure region (5), and wherein a common engine (4) is provided for driving the rotary compressor (3) and the reciprocating piston compressor (6), wherein the cylinders (7) are arranged to be rotated relative to each other by 180° in the high-pressure region (5).
Description
Multi-stage compressor The invention relates to a multi-stage compressor for compressing gases with a low-pressure region and a high-pressure region, wherein at least one rotary com-pressor is provided in the low-pressure region, and at least one reciprocating piston compressor with two cyl-inders is provided in the high-pressure region, and wherein a common engine is provided for driving the ro-tary compressor and the reciprocating piston compres-sor.
It has basically been known from WO 03/010436 Al to combine a rotary compressor, in particular a screw-type compressor, in the low-pressure region with a re-ciprocating piston compressor in the high-pressure re-gion. Here, a multi-stage reciprocating piston compres-sor is shown for high-pressure compressing of the gas to be compressed, wherein the cylinder of the individ-ual compressor stages are arranged to be V-shaped to-wards each other. Here, the reciprocating piston com-pressor and the low-pressure compressor are driven via a common crankshaft.
Furthermore, it has been known from DE 4 313 573 to provide a screw-type compressor for low-pressure compression and a high-pressure piston compressor for high-pressure compression which is driven separately of the screw-type compressor.
Moreover, a method for improving cost-effectiveness of displacement compressors has addition-ally been known from DE 199 32 433 Al, wherein it has been disclosed to drive a centrifugal compressor either by means of the driving engine of a reciprocating pis-ton compressor or by a separate engine.
Furthermore, a different vacuum pump has been known from US 4,662,826, wherein gas is first sucked off by means of a rotary vacuum pump and subsequently via a reciprocating pump coupled to the crankshaft of the rotary vacuum pump. Yet, here, no internal compres-sion of the gas to be sucked off takes place so that compared to a multi-stage high-pressure compression a possible heating of the gas to be compressed and/or a condensate accumulation is not to be considered.
Moreover, it has been basically known with piston compressors of different types to arrange the piston in boxer construction. A multi-stage piston compressor has been known from WO 2002/044564 Al for generating com-pressed air for rail vehicles, said piston compressor consisting substantially of a drive unit and a down-stream compression unit and having a low-pressure and at least one high-pressure stage. Each of the cranks provided on a crankshaft has at least two opposing pis-tons attached thereto, wherein adjacent cranks are ar-ranged to be offset relative to each other substan-tially by 180 ; here, the pistons may be arranged to be vertically upright, horizontal or V-shaped.
In DE 29 39 298 Al a reciprocating-piston-compressor plant is shown in general which comprises a boxer compressor, wherein the cylinder sleeves of a stepped cylinder are rotated by 180 and arranged oppo-sitely.
Moreover, a combined unit consisting of combustion engine and pump or compressor has been known from GB
458 333 A. The pump or compressor unit has a crankshaft with three cranks, wherein two adjacent cranks are ar-ranged to be offset relative to each other by 180 whose respective cylinders are located to oppose each other on a horizontal plane.
The object of the present invention resides in creating a multi-stage compressor of the initially de-fined type which has an improved oscillation behavior seen in contrast to comparable multi-stage compressors.
According to the invention, this is achieved in that the cylinders in the high-pressure region are ar-ranged to be rotated relative to each other by 180 .
The 180 -rotated opposite arrangement of the cylinders results in a substantially less-oscillating run of the pistons received in the cylinders for compressing the gas to be compressed. Thus, in combination with the ro-tary compressor provided in the low-pressure region, there results a highly compact multi-stage compressor which allows for a relatively high compression of a gas to be compressed to be achieved, with the oscillations generated by the multi-stage compressor being at the same time kept low. This is why the inventive multi-stage compressor is particularly suited for use in both mobile compressor plants and compressor plants mounted on a ship. Here, it is also particularly advantageous that the reciprocating piston compressor, whose at least two cylinders are rotated relative to each other by 180 , i.e. arranged in a so-called boxer construc-tion, has a center of mass which is low compared to conventional cylinders, e.g. cylinders arranged in V-shaped manner towards each other.
In order to keep the total center of mass of the multi-stage compressor as low as possible, what is of great importance with mobile compressor plants, it is furthermore advantageous if the engine is arranged lat-erally next to the reciprocating piston compressor.
Moreover, it is beneficial for a flat configuration with a consequently low center of mass if the the lon-gitudinal axis of a crankshaft of the engine is ar-ranged to be substantially horizontal as is the longi-tudinal axis of the cylinder.
As regards a particularly compact design of the multi-staged compressor, it is beneficial to provide the common engine with two shaft ends so that the ro-tary compressor and the reciprocating piston compressor can simply be coupled to the engine at opposing output sides.
Alternatively, it is also conceivable for a par-ticularly compact design to couple the rotary compres-sor to the engine-driven reciprocating piston compres-sor. In this case, only one single crankshaft is neces-sary via which both the rotary compressor and the re-ciprocating piston compressor are driven.
Since the inventive multi-stage compressor should be also particularly suited for mobile use on ships and trucks, it is beneficial if the multi-stage compressor has a comparably small span/width, without reducing its performance. This is advantageously achieved in that one stepped piston each is received in the cylinders.
Alternatively, to achieve a small span it is likewise possible to design the cylinders to be double-acting.
The comparably small span enables the multi-stage com-pressor to be advantageously received in ISO containers having a width of 8 feet (2.54 m) and a length of ei-ther 20 feet (6.079 m) or 40 feet (12.9 m). Multi-stage compressors known so far having both a rotary compres-sor and a reciprocating piston compressor, yet having the piston compressors arranged in a V-shaped manner towards each other cannot be received in ISO contain-ers, considerably complicating mobile use.
In order to restrict the final compressor tempera-ture in the high-pressure region to an admissible value, it is beneficial if the reciprocating piston compressor has several compressor stages. In case of too high a compression degree in a single compressor stage, a further compressor in a single compressor stage would be inefficient because of an increased tem-perature of the gas to be compressed.
In order to achieve an efficient control of the multi-stage compressor, it is beneficial to provide a control means between the individual compressor stages, wherein discharge valves, by-pass valves, adjustable clearances, speed governors and other instruments may be provided as control means. In particular, different mechanical, pneumatic, hydraulic, electric or elec-tronic components may be used for controlling the multi-stage compressor, thus allowing for both an on-site control and a remote control.
As regards an efficient compression in the indi-vidual compressor stages, it is beneficial to provide at least one attenuator, one cooling device, one con-densate separator, one drying device or one gas separa-tor between the individual compressor stages. Here, the "individual" compressor stages can be assigned both to the low-pressure region and the high-pressure region or they may both be assigned to the high-pressure region.
In the following, the invention will be explained in even more detail by way of the exemplary embodiments illustrated in the drawings, yet without being re-stricted thereto. Therein, in detail:
Fig. 1 shows a schematic perspective view of a multi-stage compressor, wherein a rotary compressor and a reciprocating piston compressor are arranged in boxer construction at opposing output sides of a central drive engine;
Fig. 2 shows a schematic perspective view of an-other exemplary embodiment, wherein the rotary compres-sor is coupled to the crankshaft of the reciprocating piston compressor of boxer construction;
Fig. 3 schematically shows a block diagram of a multi-stage compressor with a two-stage high-pressure compressor;
Fig. 4 shows a sectional view of another exemplary embodiment with a two-stage reciprocating piston com-pressor of boxer construction;
Fig. 5 shows a schematic sectional view of a cyl-inder with a stepped piston; and Fig. 6 shows a schematic sectional view of a dou-ble-acting cylinder.
In Fig. 1, a multi-stage compressor 1 is shown, wherein a screw-type compressor 3 is provided in a low-pressure region 2. The screw-type compressor 3 is cou-pled to a central drive engine which drives the recip-rocating piston compressor 6, likewise arranged in the high-pressure region 5, via a further crankshaft. Here, the reciprocating piston compressor 6 has two cylinders 7 arranged to be rotated relative to each other by 1800 so that the reciprocating piston compressor 6 is de-signed in a so-called "boxer construction", wherein the pistons 7' received in the cylinders 7 (cf. Fig. 3) run on the same plane of motion. Here, the neutralization of forces of inertia of first order results in a high running smoothness of the reciprocating piston compres-sor 6 so that the multi-stage compressor 1 has an im-proved oscillation behavior compared to devices known.
Moreover, a flat and short construction is achieved thereby so that the center of mass is low compared to known devices, what is particularly advantageous when using the multi-stage compressor 1 on ships.
In Fig. 2, an alternative exemplary embodiment is shown, wherein, here, the drive engine 4 has only one crankshaft 8 which drives the reciprocating piston com-pressor 6 of boxer construction via a coupling 10, with a gyrating mass 9 being interposed. Then, the screw-type compressor 3 provided in the low-pressure region 2 can be driven via the same crankshaft.
In particular, it is furthermore visible from Figs. 1 and 2 that an inlet control valve 11 is as-signed to the screw-type compressor provided in the low-pressure region 2 in conventional manner, via which valve the air inlet is controlled, and via which the air inlet will be closed when the multi-stage compres-sor 1 has been shut down. Moreover, air filter 12, oil filter 13, and fuel filter 14 of the drive engine 4 can be seen. Yet, what is substantial here is only the ar-rangement of the two cylinders 7 of the reciprocating piston compressor 6 in boxer construction.
In the block diagram of Fig. 3, it can be seen that a cooling device 15 is provided between the rotary compressor or screw-type compressor 3 in the low-pressure region 2 and the high-pressure region 5 in which a reciprocating piston compressor 6 with two compressor stages 6', 6" is located, said cooling device serving for cooling the gas which has an increased temperature due to internal compression, and that a condensate separator 16 is provided downstream thereof so as to allow for an efficient compression in the downstream high-pressure region 5. Furthermore, a pulsation at-tenuator 17 is provided for limiting the pressure os-cillations of the gas to be compressed. Subsequently, the already pre-compressed gas enters the high-pressure region 5 in which a multi-stage piston compressor 6 is located having two opposing cylinders 7 and pistons 7' in each compressor stage 6', 6" so that - in addition to the compact construction of the multi-stage compres-sor 1 and the high compression efficiency - a high run-ning smoothness of the whole assembly is ensured, mak-ing the multi-stage compressor 1 particularly suitable for use in mobile compressor plants and on ships.
In Fig. 4, another exemplary embodiment of the multi-stage compressor 1 is shown, wherein the cen-trally arranged common engine 4 is particularly visible which has a crankshaft 8 with two stub shafts 8', wherein a screw-type compressor is driven in the low-pressure region 2 via one stub shaft 8', with the two-stage reciprocating piston compressor 6 being driven via the other stub shaft 81.
The two compressor stages 61, 6" of the recipro-cating piston compressor 6 of boxer construction, as can be seen in Figs. 5 and 6, may be designed to be a stepped piston 15 or a double-acting cylinder 16. These two embodiment variants allow for a comparably short construction of the reciprocating piston compressor 6 to be achieved, thus enabling a comparably small span of the whole assembly 1 to be achieved with the ar-rangement of the cylinders 7 in the high-pressure re-gion 5 in a manner rotated 1800 relative to each other according to the invention, since the reciprocating piston compressor 6 has the largest width of the whole assembly 1. In particular, this allows for the instal-lation of multi-stage compressors 1 in ISO containers having a width of 8 feet (2.44 m), what - together wit the low center of mass of the whole assembly - consti-tutes a great advantage as regards mobile use, in par-ticular on ships.
It has basically been known from WO 03/010436 Al to combine a rotary compressor, in particular a screw-type compressor, in the low-pressure region with a re-ciprocating piston compressor in the high-pressure re-gion. Here, a multi-stage reciprocating piston compres-sor is shown for high-pressure compressing of the gas to be compressed, wherein the cylinder of the individ-ual compressor stages are arranged to be V-shaped to-wards each other. Here, the reciprocating piston com-pressor and the low-pressure compressor are driven via a common crankshaft.
Furthermore, it has been known from DE 4 313 573 to provide a screw-type compressor for low-pressure compression and a high-pressure piston compressor for high-pressure compression which is driven separately of the screw-type compressor.
Moreover, a method for improving cost-effectiveness of displacement compressors has addition-ally been known from DE 199 32 433 Al, wherein it has been disclosed to drive a centrifugal compressor either by means of the driving engine of a reciprocating pis-ton compressor or by a separate engine.
Furthermore, a different vacuum pump has been known from US 4,662,826, wherein gas is first sucked off by means of a rotary vacuum pump and subsequently via a reciprocating pump coupled to the crankshaft of the rotary vacuum pump. Yet, here, no internal compres-sion of the gas to be sucked off takes place so that compared to a multi-stage high-pressure compression a possible heating of the gas to be compressed and/or a condensate accumulation is not to be considered.
Moreover, it has been basically known with piston compressors of different types to arrange the piston in boxer construction. A multi-stage piston compressor has been known from WO 2002/044564 Al for generating com-pressed air for rail vehicles, said piston compressor consisting substantially of a drive unit and a down-stream compression unit and having a low-pressure and at least one high-pressure stage. Each of the cranks provided on a crankshaft has at least two opposing pis-tons attached thereto, wherein adjacent cranks are ar-ranged to be offset relative to each other substan-tially by 180 ; here, the pistons may be arranged to be vertically upright, horizontal or V-shaped.
In DE 29 39 298 Al a reciprocating-piston-compressor plant is shown in general which comprises a boxer compressor, wherein the cylinder sleeves of a stepped cylinder are rotated by 180 and arranged oppo-sitely.
Moreover, a combined unit consisting of combustion engine and pump or compressor has been known from GB
458 333 A. The pump or compressor unit has a crankshaft with three cranks, wherein two adjacent cranks are ar-ranged to be offset relative to each other by 180 whose respective cylinders are located to oppose each other on a horizontal plane.
The object of the present invention resides in creating a multi-stage compressor of the initially de-fined type which has an improved oscillation behavior seen in contrast to comparable multi-stage compressors.
According to the invention, this is achieved in that the cylinders in the high-pressure region are ar-ranged to be rotated relative to each other by 180 .
The 180 -rotated opposite arrangement of the cylinders results in a substantially less-oscillating run of the pistons received in the cylinders for compressing the gas to be compressed. Thus, in combination with the ro-tary compressor provided in the low-pressure region, there results a highly compact multi-stage compressor which allows for a relatively high compression of a gas to be compressed to be achieved, with the oscillations generated by the multi-stage compressor being at the same time kept low. This is why the inventive multi-stage compressor is particularly suited for use in both mobile compressor plants and compressor plants mounted on a ship. Here, it is also particularly advantageous that the reciprocating piston compressor, whose at least two cylinders are rotated relative to each other by 180 , i.e. arranged in a so-called boxer construc-tion, has a center of mass which is low compared to conventional cylinders, e.g. cylinders arranged in V-shaped manner towards each other.
In order to keep the total center of mass of the multi-stage compressor as low as possible, what is of great importance with mobile compressor plants, it is furthermore advantageous if the engine is arranged lat-erally next to the reciprocating piston compressor.
Moreover, it is beneficial for a flat configuration with a consequently low center of mass if the the lon-gitudinal axis of a crankshaft of the engine is ar-ranged to be substantially horizontal as is the longi-tudinal axis of the cylinder.
As regards a particularly compact design of the multi-staged compressor, it is beneficial to provide the common engine with two shaft ends so that the ro-tary compressor and the reciprocating piston compressor can simply be coupled to the engine at opposing output sides.
Alternatively, it is also conceivable for a par-ticularly compact design to couple the rotary compres-sor to the engine-driven reciprocating piston compres-sor. In this case, only one single crankshaft is neces-sary via which both the rotary compressor and the re-ciprocating piston compressor are driven.
Since the inventive multi-stage compressor should be also particularly suited for mobile use on ships and trucks, it is beneficial if the multi-stage compressor has a comparably small span/width, without reducing its performance. This is advantageously achieved in that one stepped piston each is received in the cylinders.
Alternatively, to achieve a small span it is likewise possible to design the cylinders to be double-acting.
The comparably small span enables the multi-stage com-pressor to be advantageously received in ISO containers having a width of 8 feet (2.54 m) and a length of ei-ther 20 feet (6.079 m) or 40 feet (12.9 m). Multi-stage compressors known so far having both a rotary compres-sor and a reciprocating piston compressor, yet having the piston compressors arranged in a V-shaped manner towards each other cannot be received in ISO contain-ers, considerably complicating mobile use.
In order to restrict the final compressor tempera-ture in the high-pressure region to an admissible value, it is beneficial if the reciprocating piston compressor has several compressor stages. In case of too high a compression degree in a single compressor stage, a further compressor in a single compressor stage would be inefficient because of an increased tem-perature of the gas to be compressed.
In order to achieve an efficient control of the multi-stage compressor, it is beneficial to provide a control means between the individual compressor stages, wherein discharge valves, by-pass valves, adjustable clearances, speed governors and other instruments may be provided as control means. In particular, different mechanical, pneumatic, hydraulic, electric or elec-tronic components may be used for controlling the multi-stage compressor, thus allowing for both an on-site control and a remote control.
As regards an efficient compression in the indi-vidual compressor stages, it is beneficial to provide at least one attenuator, one cooling device, one con-densate separator, one drying device or one gas separa-tor between the individual compressor stages. Here, the "individual" compressor stages can be assigned both to the low-pressure region and the high-pressure region or they may both be assigned to the high-pressure region.
In the following, the invention will be explained in even more detail by way of the exemplary embodiments illustrated in the drawings, yet without being re-stricted thereto. Therein, in detail:
Fig. 1 shows a schematic perspective view of a multi-stage compressor, wherein a rotary compressor and a reciprocating piston compressor are arranged in boxer construction at opposing output sides of a central drive engine;
Fig. 2 shows a schematic perspective view of an-other exemplary embodiment, wherein the rotary compres-sor is coupled to the crankshaft of the reciprocating piston compressor of boxer construction;
Fig. 3 schematically shows a block diagram of a multi-stage compressor with a two-stage high-pressure compressor;
Fig. 4 shows a sectional view of another exemplary embodiment with a two-stage reciprocating piston com-pressor of boxer construction;
Fig. 5 shows a schematic sectional view of a cyl-inder with a stepped piston; and Fig. 6 shows a schematic sectional view of a dou-ble-acting cylinder.
In Fig. 1, a multi-stage compressor 1 is shown, wherein a screw-type compressor 3 is provided in a low-pressure region 2. The screw-type compressor 3 is cou-pled to a central drive engine which drives the recip-rocating piston compressor 6, likewise arranged in the high-pressure region 5, via a further crankshaft. Here, the reciprocating piston compressor 6 has two cylinders 7 arranged to be rotated relative to each other by 1800 so that the reciprocating piston compressor 6 is de-signed in a so-called "boxer construction", wherein the pistons 7' received in the cylinders 7 (cf. Fig. 3) run on the same plane of motion. Here, the neutralization of forces of inertia of first order results in a high running smoothness of the reciprocating piston compres-sor 6 so that the multi-stage compressor 1 has an im-proved oscillation behavior compared to devices known.
Moreover, a flat and short construction is achieved thereby so that the center of mass is low compared to known devices, what is particularly advantageous when using the multi-stage compressor 1 on ships.
In Fig. 2, an alternative exemplary embodiment is shown, wherein, here, the drive engine 4 has only one crankshaft 8 which drives the reciprocating piston com-pressor 6 of boxer construction via a coupling 10, with a gyrating mass 9 being interposed. Then, the screw-type compressor 3 provided in the low-pressure region 2 can be driven via the same crankshaft.
In particular, it is furthermore visible from Figs. 1 and 2 that an inlet control valve 11 is as-signed to the screw-type compressor provided in the low-pressure region 2 in conventional manner, via which valve the air inlet is controlled, and via which the air inlet will be closed when the multi-stage compres-sor 1 has been shut down. Moreover, air filter 12, oil filter 13, and fuel filter 14 of the drive engine 4 can be seen. Yet, what is substantial here is only the ar-rangement of the two cylinders 7 of the reciprocating piston compressor 6 in boxer construction.
In the block diagram of Fig. 3, it can be seen that a cooling device 15 is provided between the rotary compressor or screw-type compressor 3 in the low-pressure region 2 and the high-pressure region 5 in which a reciprocating piston compressor 6 with two compressor stages 6', 6" is located, said cooling device serving for cooling the gas which has an increased temperature due to internal compression, and that a condensate separator 16 is provided downstream thereof so as to allow for an efficient compression in the downstream high-pressure region 5. Furthermore, a pulsation at-tenuator 17 is provided for limiting the pressure os-cillations of the gas to be compressed. Subsequently, the already pre-compressed gas enters the high-pressure region 5 in which a multi-stage piston compressor 6 is located having two opposing cylinders 7 and pistons 7' in each compressor stage 6', 6" so that - in addition to the compact construction of the multi-stage compres-sor 1 and the high compression efficiency - a high run-ning smoothness of the whole assembly is ensured, mak-ing the multi-stage compressor 1 particularly suitable for use in mobile compressor plants and on ships.
In Fig. 4, another exemplary embodiment of the multi-stage compressor 1 is shown, wherein the cen-trally arranged common engine 4 is particularly visible which has a crankshaft 8 with two stub shafts 8', wherein a screw-type compressor is driven in the low-pressure region 2 via one stub shaft 8', with the two-stage reciprocating piston compressor 6 being driven via the other stub shaft 81.
The two compressor stages 61, 6" of the recipro-cating piston compressor 6 of boxer construction, as can be seen in Figs. 5 and 6, may be designed to be a stepped piston 15 or a double-acting cylinder 16. These two embodiment variants allow for a comparably short construction of the reciprocating piston compressor 6 to be achieved, thus enabling a comparably small span of the whole assembly 1 to be achieved with the ar-rangement of the cylinders 7 in the high-pressure re-gion 5 in a manner rotated 1800 relative to each other according to the invention, since the reciprocating piston compressor 6 has the largest width of the whole assembly 1. In particular, this allows for the instal-lation of multi-stage compressors 1 in ISO containers having a width of 8 feet (2.44 m), what - together wit the low center of mass of the whole assembly - consti-tutes a great advantage as regards mobile use, in par-ticular on ships.
Claims (8)
1. A multi-stage compressor (1) for compressing gases with a low-pressure region (2) and a high-pressure re-gion (5), wherein at least one screw-type compressor (3) is provided in the low-pressure region (2), and at least one reciprocating piston compressor (6) with two cylinders (7) is provided in the high-pressure region (5), and wherein a common engine (4) is provided for driving the screw-type compressor (3) and the recipro-cating piston compressor (6), wherein the longitudinal axis of a crankshaft (8) of the engine (4) is arranged to be substantially horizontal, and the engine (4) is arranged laterally next to the reciprocating piston compressor (6), characterized in that one stepped pis-ton each is received in the cylinders (7) or the cylin-ders (7) are designed to be double-acting, and the cyl-inders (7) are arranged to be rotated relative to each other by 180° in the high-pressure region (5), with the longitudinal axis of said cylinders (7) extending sub-stantially horizontally.
2. The multi-stage compressor according to claim 1, characterized in that the rotary compressor (3) and the reciprocating piston compressor (6) are coupled to the engine (4) at the opposing output sides.
3. The multi-stage compressor according to claim 1 or 2, characterized in that the rotary compressor (3) is coupled to the engine-driven reciprocating piston com-pressor (6).
4. The multi-stage compressor according to any one of claims 1 to 3, characterized in that the reciprocating piston compressor (6) has several compressor stages (6' 6'').
5. The multi-stage compressor according to any one of claims 1 to 4, characterized in that at least one con-trol means is provided between the individual compres-sor stages (2, 5; 6', 6'').
6. The multi-stage compressor according to any one of claims 1 to 5, characterized in that at least one at-tenuator (17), one cooling device (15), one condensate separator (16), one drying device or one gas separator is provided between the individual compressor stages (2, 5; 6', 6'') .
7. Use of a multi-stage compressor according to any one of claims 1 to 6 in a mobile compressor plant.
8. Use of a multi-stage compressor according to any one of claims 1 to 6 in a compressor plant mounted on a ship.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT0062006U AT9916U1 (en) | 2006-08-16 | 2006-08-16 | MULTI-STAGE COMPRESSOR |
| ATGM620/2006 | 2006-08-16 | ||
| PCT/AT2007/000392 WO2008019416A1 (en) | 2006-08-16 | 2007-08-16 | Multi-stage compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2660494A1 true CA2660494A1 (en) | 2008-02-21 |
| CA2660494C CA2660494C (en) | 2014-10-21 |
Family
ID=39048744
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2660494A Active CA2660494C (en) | 2006-08-16 | 2007-08-16 | Multi-stage compressor |
Country Status (12)
| Country | Link |
|---|---|
| US (3) | US8376717B2 (en) |
| EP (1) | EP2052156B1 (en) |
| AT (2) | AT9916U1 (en) |
| CA (1) | CA2660494C (en) |
| DE (1) | DE502007001876D1 (en) |
| DK (1) | DK2052156T3 (en) |
| EA (1) | EA014462B1 (en) |
| ES (1) | ES2335944T3 (en) |
| NO (1) | NO337971B1 (en) |
| PL (1) | PL2052156T3 (en) |
| PT (1) | PT2052156E (en) |
| WO (1) | WO2008019416A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT9916U1 (en) * | 2006-08-16 | 2008-05-15 | Leobersdorfer Maschf | MULTI-STAGE COMPRESSOR |
| EP2105649B1 (en) * | 2008-03-28 | 2013-01-30 | Neuman & Esser Deutschland GmbH & Co. KG | Machine framework |
| DE102011121055A1 (en) * | 2011-12-14 | 2013-06-20 | Wabco Gmbh | Multistage compressor i.e. two-stage compressor, for pneumatic spring system of passenger car, has common electrical drive unit with common drive shaft for driving both compaction stages, and rotor arranged coaxial to drive shaft |
| JP6178671B2 (en) * | 2013-08-26 | 2017-08-09 | 川崎重工業株式会社 | Cylinder head bolt fastening structure |
| RU2722116C1 (en) * | 2019-09-18 | 2020-05-26 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Омский государственный технический университет"(ОмГТУ) | Method of piston two-stage compressor operation and device for implementation thereof |
| DE102019126103A1 (en) * | 2019-09-27 | 2021-04-01 | Amk Holding Gmbh & Co. Kg | Air compressor for a vehicle |
| US11549496B2 (en) * | 2019-11-15 | 2023-01-10 | Estis Compression, LLC | Reconfigurable multi-stage gas compressor |
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| US341099A (en) * | 1886-05-04 | Air-compressor | ||
| GB597437A (en) * | 1945-08-17 | 1948-01-26 | Arthur Cyril Thornton | Improvements in or relating to air compressors for aircraft |
| US1388780A (en) * | 1920-11-29 | 1921-08-23 | Arthur E Stanley | Pump |
| US1855673A (en) * | 1928-05-11 | 1932-04-26 | Hansen Paul | Compressor plant |
| GB458333A (en) | 1936-02-18 | 1936-12-17 | Crossley Premier Engines Ltd | Improvements relating to combined internal combustion engine and pump or compressor units |
| FR944598A (en) * | 1941-04-01 | 1949-04-08 | Improvements to reciprocating compressors | |
| US2702008A (en) * | 1952-06-09 | 1955-02-15 | John M Stockard | Pumping apparatus |
| FR1231185A (en) * | 1959-04-09 | 1960-09-27 | Piston air compressor | |
| US3744936A (en) * | 1968-03-13 | 1973-07-10 | Lear Siegler Inc | Piston type pump |
| CA1081189A (en) * | 1976-11-08 | 1980-07-08 | Diver's Exchange | Breathing gas pump apparatus for divers |
| DD147787A3 (en) | 1978-10-25 | 1981-04-22 | Manfred Malick | RECIPROCATING SYSTEM |
| US4662826A (en) * | 1984-04-20 | 1987-05-05 | Tokico Ltd. | Vacuum pump system including serially connected rotary and reciprocating vacuum pumps |
| JPS60233379A (en) * | 1984-04-21 | 1985-11-20 | Showa Seiki Kogyo Kk | Reciprocating gas compressor |
| US4789310A (en) * | 1987-01-08 | 1988-12-06 | Michael Hung | Multi-function implement for illumination and air-supply |
| US4756674A (en) * | 1987-08-24 | 1988-07-12 | Ingersoll-Rand Company | Reciprocating gas compressor having a split housing and crosshead guide means |
| DE4313573A1 (en) | 1993-04-26 | 1994-10-27 | Leobersdorfer Maschf | Reduce condensation of water vapor and expel condensate while compressing air |
| DE19932433A1 (en) | 1999-07-12 | 2000-01-27 | Regar Karl Nikolaus | Economy improvement process for displacement compressors, involving charging normally free-induction compressors using low-pressure centrifugal pre-compressors |
| DE19947444A1 (en) * | 1999-10-02 | 2001-04-05 | Messer Griesheim Gmbh | New gas pump, useful for collection of used anesthesia gases, comprises a compressor unit with controllable temperature |
| DE10058924C2 (en) | 2000-11-28 | 2002-11-21 | Knorr Bremse Systeme | Low-vibration multi-stage piston compressor |
| GB2394259B (en) * | 2001-07-25 | 2005-05-25 | Leobersdorfer Maschf | Multistage compressor for compressing gases |
| AT9916U1 (en) * | 2006-08-16 | 2008-05-15 | Leobersdorfer Maschf | MULTI-STAGE COMPRESSOR |
-
2006
- 2006-08-16 AT AT0062006U patent/AT9916U1/en not_active IP Right Cessation
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2007
- 2007-08-16 WO PCT/AT2007/000392 patent/WO2008019416A1/en active Application Filing
- 2007-08-16 CA CA2660494A patent/CA2660494C/en active Active
- 2007-08-16 DK DK07784621.0T patent/DK2052156T3/en active
- 2007-08-16 AT AT07784621T patent/ATE447108T1/en active
- 2007-08-16 DE DE502007001876T patent/DE502007001876D1/en active Active
- 2007-08-16 PL PL07784621T patent/PL2052156T3/en unknown
- 2007-08-16 US US12/374,685 patent/US8376717B2/en active Active
- 2007-08-16 ES ES07784621T patent/ES2335944T3/en active Active
- 2007-08-16 EA EA200970153A patent/EA014462B1/en unknown
- 2007-08-16 PT PT07784621T patent/PT2052156E/en unknown
- 2007-08-16 EP EP07784621A patent/EP2052156B1/en not_active Revoked
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2009
- 2009-02-09 NO NO20090600A patent/NO337971B1/en unknown
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2013
- 2013-01-25 US US13/749,752 patent/US8708666B2/en active Active
- 2013-01-25 US US13/749,750 patent/US8568107B2/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| US8708666B2 (en) | 2014-04-29 |
| EA014462B1 (en) | 2010-12-30 |
| CA2660494C (en) | 2014-10-21 |
| US8376717B2 (en) | 2013-02-19 |
| US20130164151A1 (en) | 2013-06-27 |
| NO20090600L (en) | 2009-02-09 |
| PL2052156T3 (en) | 2010-05-31 |
| DE502007001876D1 (en) | 2009-12-10 |
| EP2052156B1 (en) | 2009-10-28 |
| EA200970153A1 (en) | 2009-06-30 |
| NO337971B1 (en) | 2016-07-18 |
| EP2052156A1 (en) | 2009-04-29 |
| DK2052156T3 (en) | 2010-03-15 |
| US20130164150A1 (en) | 2013-06-27 |
| US20110164990A1 (en) | 2011-07-07 |
| WO2008019416A1 (en) | 2008-02-21 |
| ES2335944T3 (en) | 2010-04-06 |
| PT2052156E (en) | 2010-02-01 |
| US8568107B2 (en) | 2013-10-29 |
| AT9916U1 (en) | 2008-05-15 |
| ATE447108T1 (en) | 2009-11-15 |
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